Support Roller, Vehicle with A Support Roller and Method for Stabilizing A Vehicle

ABSTRACT

A support roller ( 30, 30 ′) for supporting a vehicle on an underlying surface, comprising at least one bearing element which is at least indirectly connectable to at least one supporting structure of the vehicle, at least one fork connected to the bearing element, and at least one wheel ( 90, 90 ′) which is mounted in the fork so as to be rotatable about a first rolling axis (R) and can be brought into contact with the underlying surface, at least one sensing device ( 190 ) for sensing at least one supporting force with which the wheel ( 90, 90 ′) is supported on the underlying surface. A vehicle, in particular an industrial truck, comprising at least one support roller and a method for stabilizing a vehicle.

The present invention relates to a support roller for supporting avehicle on an underlying surface, comprising at least one bearingelement connectable at least indirectly to at least one supportingstructure of the vehicle, at least one fork connected to the bearingelement and at least one wheel mounted in the fork so as to be rotatableabout a first rolling axis and be brought into contact with theunderlying surface. The present invention also relates to a vehicle withsuch a support roller and a method for stabilizing a vehicle.

A wide variety of vehicles for transporting loads are known from theprior art. For example, industrial trucks with rollers run on anunderlying surface, floor or open surface, can be steered and are mostlyused for internal transport. Depending on the individual design,industrial trucks can also be used for lifting and stacking loads. Awell-known design uses a five-wheel chassis, where a drive wheel drivesthe industrial truck and support rollers ensure the stability of theindustrial truck. The main purpose of these support rollers is to givethe industrial truck lateral stability against tipping over. The risk oftipping over exists, for example, when cornering tightly andsimultaneously lifting and transporting loads, wherein the center ofgravity of the industrial truck is unfavorably shifted in the directionof the load from the underlying surface on which the industrial truck ismoved. The use of a spring-loaded axle rotatable about a rotary axis, aso-called coupling rocker, at the end-areas of which support rollers arearranged, is known from prior art as a stabilization element forlimiting the lateral inclination. For example, the DE 20 2015 103 436.9,which was not previously published, describes such a coupling rocker.The object of the coupling rocker is to distribute the supporting forceevenly over the support rollers according to the driving situation.

However, the solutions known from the prior art have the disadvantagethat when the vehicle tilts to one side, the coupling rocker movesupwards in the opposite direction to the underlying surface or isrotated, so that the entire spring force of the coupling rocker actsonly on one support roller, wherein the other support roller on thecoupling rocker is relieved accordingly and held at a distance from theunderlying surface.

The object of the present invention is therefore to provide a supportroller which, when used in a vehicle, in particular an industrial truck,enables increased stability to be achieved so as to overcome thedisadvantages of the prior art, in particular to prevent excessivetilting of the industrial truck and thus reduce the risk of tippingover.

This object is solved according to the invention by at least one sensingdevice to detect at least one supporting force with which the wheelrests on the underlying surface.

It may be provided that the rolling axis is perpendicular to a normaldirection of the underlying surface and/or that the supporting structureis formed at least in certain areas by a part of the vehicle body.

It is further proposed that the bearing element is formed in the form ofat least one rotary bearing and that a rotation of the fork about apivot axis running substantially perpendicularly to the rolling axis ispossible by means of the rotary bearing, wherein in particular therolling axis and the pivot axis intersect or run obliquely relative toone another and/or the fork and/or the rolling axis can be forced bymeans of at least one first return device into at least onepredetermined position relative to the bearing element and/or thesupporting structure, preferably with regard to the pivot axis.

It is also preferable that a movement of at least one first elementrelative to at least one second element is detectable by means of thesensing device, preferably that a, in particular linear, movement in afirst direction running perpendicularly to the rolling axis and/orparallel to the pivot axis, and/or a force acting by means of thesensing device between the first element and the second element, inparticular a tensile force, a compressive force and/or shear force, isdetectable.

In the aforementioned embodiment, it is particularly preferred that thefirst element is selected from the group comprising the roller, abearing axle of the roller mounted in the fork, the fork, at least oneconnecting means of the fork to the bearing element, such as a pin, andthe bearing element, and/or the second element is selected from thegroup comprising the bearing axle, the fork, the connecting means, thebearing element and the supporting structure.

It is also proposed for the two aforementioned embodiments that thesecond element, in particular the bearing element, is adapted to keepthe first element, in particular the fork, movable along the firstdirection, preferably the second element is adapted to allow a movementof the first element of up to 5 mm, in particular of 3 mm, preferablyrelative to the second element.

Furthermore, an inventive support roller can be characterized in thatthe first element, in particular the fork and/or the connecting means,can be forced into a first position, in particular in a directiontowards the second element, by means of at least one second returndevice.

It is also preferred that the first return device and/or the secondreturn device comprises at least one elastic means, at least onecompression spring, at least one helical spring, at least one pneumaticspring, at least one hydraulic spring and/or at least one gas pressurespring.

Preferred embodiments of the invention provide for the sensing device tobe arranged at least in certain areas in the bearing element and/or onthe side of the bearing element, preferably the pivot bearing, facingaway from the fork and/or the wheel.

An inventive support roller can also be characterized by at least oneposition recognition device by means of which an alignment of the fork,the bearing axis and/or the wheel about the pivot axis and/or relativeto the underlying surface is determinable.

An inventive support roller can finally be characterized in that thesensing device and/or the position recognition device comprises and/orcomprise at least one sensor means, in particular comprising at leastone limit switch, at least one strain gauge sensor, at least onepressure sensor, at least one Hall sensor, at least one radar sensor, atleast one ultrasonic sensor, at least one distance sensor, at least oneecho sounder sensor, at least one acoustic sensor, at least one opticalsensor, at least one electromagnetic sensor, and/or at least onemagnetic sensor, or and/or the first position and/or at least a secondposition of the first element relative to the second element isdetectable by means of the sensing device.

Furthermore, the invention provides a vehicle, in particular anindustrial truck, comprising at least one inventive support roller.

In this case the invention suggests that the vehicle further comprisesat least one coupling rocker, the coupling rocker being arrangedmechanically between the supporting structure and the support roller,and the coupling rocker having at least one rocker which is mountedrotatably about at least one rotary axis and a lever which isoperatively connected to the rocker, wherein the support roller, inparticular the bearing element, is supported at the end of the leverfacing away from the pivot axis and/or the rocker, wherein furthermorethe lever is preferably surrounded by the rocker and/or is formedintegrally with the rocker at least in certain areas.

Here it is particularly preferred that the coupling rocker comprises atleast one third return device by means of which the rocker and/or thelever is/are forceable into at least one third position, wherein thethird return device preferably comprises at least one torsion spring, atleast one helical spring, at least one tension spring, at least onethrust spring, at least one shear spring, at least one rubber-elasticelement, at least one spiral spring and/or at least one gas pressurespring.

In the two aforementioned embodiments, it is particularly preferred thatthe coupling rocker comprises at least one shock absorbing device,wherein a movement, in particular of the lever, the support rollerand/or the rocker about the rotary axis can be cushioned by means of theshock absorbing device.

Furthermore, an inventive vehicle can be characterized by at least onecontrol member, which is in particular in operative connection with theshock absorbing device, wherein a movement, in particular of the lever,the support roller and/or the rocker, about the rotary axis by means ofthe control member is reducible, preferably suppressible, wherein thecontrol member is preferably at least in certain areas enclosed by theshock absorbing device.

It is also proposed with the invention that the shock absorbing deviceand/or the control member comprises at least one cylinder, in particulara hydraulic cylinder, with at least one piston movable within thecylinder, the cylinder being operatively connected to the lever, thesupport roller, in particular the bearing element, and/or the rocker,preferably via a connecting element extending at least in a radialdirection with respect to the rotary axis, and the piston beingoperatively connected to the supporting structure or the piston beingoperatively connected to the lever, the rocker, the support roller, thebearing element and/or the connecting element and the cylinder beingoperatively connected to the supporting structure.

In the aforementioned embodiment it is particularly preferable that thecontrol member comprises at least one control element, wherein thecontrol element preferably comprises at least one control valve and/or,by means of closing the control element, a movement of the shockabsorbing device and/or of the control member and/or a movement, inparticular of the rocker, of the lever and/or of the support roller,about the rotary axis is prevented and, when the control element isopened, a movement of the shock absorbing device and/or of the controlmember and/or a movement, in particular of the rocker, of the leverand/or of the support roller, about the rotary axis is released.

Furthermore, the invention proposes that an inventive vehicle ischaracterized in that the cylinder preferably comprises a single-actingcylinder and the control element comprises a throttle element adapted tocontrol the flow rate of at least one fluid, preferably a hydraulicfluid, a gas and/or air into the cylinder, preferably to allow shockabsorbing, preferably the control element being adapted to control thethrottle element as a function of the supporting force detected by thesensing device in order to increase the fluid pressure in order to avoida reduction of the supporting force below a predetermined value.

The invention also proposes that the cylinder, in particular thehydraulic cylinder, comprises at least two-cylinder chambers connectibleto each other via at least one throttle, the fluid being movable inparticular between the cylinder chambers, in particular by movement ofthe piston.

Furthermore, the invention proposes that the control member comprises atleast one braking means, in particular an electromagnetic brake, amechanical brake, an adhesive and/or positive brake, the braking meansbeing operatively connected, preferably on the one hand, to the rockerand/or to the support roller and/or, on the other hand, to thesupporting structure.

In the aforementioned embodiment it is particularly preferred that thebraking means is arranged, at least in certain areas, preferablycircularly revolving around the rotary axis of the coupling rocker.

The invention further proposes that at least one control deviceoperatively connected to the control member and/or the shock absorbingdevice, the control device comprising at least one power supply, inparticular an electrical voltage supply and/or a device for storingand/or emitting mechanical energy, of the braking means, and whereinwhen energy is emitted from the control device to the control member amovement of the shock absorbing device and/or of the control memberand/or a movement, in particular of the rocker and/or of the supportroller, about the rotary axis is prevented, and when the emission ofenergy is interrupted a movement of the shock absorbing device and/or ofthe control member and/or a movement, in particular of the rocker and/orof the support roller, about the rotary axis is enabled.

Furthermore, the invention suggests that an inventive vehicle ischaracterized by at least one control device operatively connected tothe sensing device, the position recognition device, the control deviceand/or the control member, preferably the control element, wherein thecontrol member can preferably be influenced by means of the controldevice in such a way that the movement about the rotary axis is reduced,is preferably prevented when, by means of the sensing device, asupporting force is sensed which corresponds to a missing contactbetween the support roller and the underlying surface and/or themovement about the rotary axis is at least partially released when, bymeans of the sensing device, a supporting force is sensed whichcorresponds to an existing contact between the support roller and theunderlying surface.

In the aforementioned embodiment, it is particularly preferred that thecontrol device influences the control member as a function of a positionof at least one lifting fork of the vehicle, in particular relative tothe underlying surface, a speed of the vehicle and/or a steering angleof the vehicle.

Furthermore, the invention proposes that the control member comprises atleast one pump means for increasing a fluid pressure in the cylinder, inparticular the cylinder chambers, preferably the control device beingadapted to control the pump means as a function of the supporting forcedetected by the sensing device in order to increase the fluid pressurein order to avoid a reduction of the supporting force below apredetermined value.

Particularly preferred embodiments of the vehicle may be characterizedby a plurality of support rollers according to any of claims 1 to 11,wherein the coupling rocker preferably comprises a plurality of levers,preferably arranged on the rocker, surrounded by the rocker and/or atleast in certain areas integrally formed with the rocker.

Finally, it is proposed for the inventive vehicle that the vehicle isformed as an industrial truck and/or as a pallet truck with at least onedrive wheel, in particular a pallet truck with five-wheel chassis.

Finally, the invention provides a method for stabilizing a vehicle, inparticular an inventive vehicle, with a coupling rocker and at least onesupport roller, in particular an inventive support roller, comprisingthe following steps:

Recognizing a supporting force with which the support roller issupported on an underlying surface, the support roller being in contactwith the underlying surface in the case of at least one first supportingforce, and the support roller being in no contact with the underlyingsurface in the case of at least one second supporting force; and controlof a control member as a function of the recognized supporting force, arotation of the coupling rocker and/or of the support roller about arotary axis being at least partially prevented by means of the controlmember when the second supporting force is recognized.

The invention also proposes for the method that, when the firstsupporting force is recognized, a movement about the rotary axis iscushioned by means of at least one shock absorbing device.

In the case of the two aforementioned embodiments, it is particularlypreferred that the cushioning and suppression of the movement about therotary axis is carried out by means of a device which at least in partcomprises the control member and the shock absorbing device, inparticular the shock absorbing device and the control member are atleast in part formed integrally.

Finally, it is proposed for the method that the suppression of themovement about the rotary axis is achieved by suppressing a movement ofthe shock absorbing device and/or at least a third return device.

The term “body part” or “supporting structure” can also be used todescribe an attachment to a component of the vehicle.

The invention is therefore based on the surprising realization that byproviding a support roller which makes it possible to determine asupporting force with which a wheel of the support roller is supportedon an underlying surface, the stability of a vehicle in which thesupport roller is installed can be increased by limiting an inclinationof the vehicle, in particular of an industrial truck.

This means that an inclination of the vehicle can be proactivelycounteracted before the inclination becomes so critical that the vehiclecould fall over. This effect is achieved in particular by combining theinventive support roller with a coupling rocker and limiting a rotarymovement of the coupling rocker around a rotary axis when the supportroller lifts off from the underlying surface. This is sensed bydetecting a supporting force below a threshold value by means of theinventive sensing device, so that a lift-off of the support roller fromthe underlying surface can be inferred. This limitation of the rotarymovement of the coupling rocker can be achieved in particular bychanging the behavior of a shock absorbing device. It is alsoconceivable that a control member is used which limits the rotarymovement of the coupling rocker, for example by using mechanical lockingin at least one predetermined position, preferably a plurality ofpositions, of the coupling rocker about the rotary axis. This effect oflimiting or blocking the rotary motion of the coupling rocker about therotary axis is preferably achieved by a cylinder linkage on the couplingrocker, whereby the inclination of the vehicle can be limited.

Within the meaning of the invention, the term “underlying surface” isused to refer in particular to the floor on which the support roller issupported or on which the vehicle is moved. The term “the support rollerhas no contact with the underlying surface” can therefore be used todefine that the support roller is free in the air and that theindustrial truck does not exert a support load on the support roller.This position of the support roller is detected by the sensing devicedetecting that the supporting force is below a predetermined threshold.Contact with the underlying surface occurs when the sensed supportingforce exceeds a predetermined threshold value. The term “cushioningmovement about the rotary axis” is used in particular to describe acushioned up- and down-movement of the coupling rocker or a suspensionof the coupling rocker. The term “arranged in a spring-loaded manner”can be used according to the invention to define that the coupling armis arranged on a load-bearing body part in such a way that it is movableor spring-loaded at least in the vertical direction. The spring bearingcan be achieved by a spring-loaded suspension of the coupling rockerand/or by the hydraulic cylinder or an additional return device, such asa torsion spring.

Recognizing whether the vehicle is neutral or inclined can be carriedout simply by detecting the underlying surface contact of the supportrollers by sensing the supporting force.

According to the invention, the support roller can be a fixed roller.With such a fixed roller, the bearing element is configured in such away that a rotation of the fork or wheel about the pivot axis relativeto the bearing element is prevented. Alternatively, the support rollercan also be formed as a free-rotating support roller, in which thebearing element then has the shape of a pivot bearing and allows thefork or wheel to rotate about the pivot axis. The support roller canalso be formed as a positively steered roller. This means that aposition of the fork or the wheel around the pivot axis can becontrolled or regulated by means of an actuator device. The inventivesupport roller can generally also be freely pivoted, but can be forcedinto at least one predetermined position, for example a straightextension position of the vehicle, by means of a first return device, inparticular a spiral spring. In particular, if the support roller is incontact with the underlying surface, it will be forced in the drivingdirection against the force of the first return device. If, however, thesupport roller loses contact with the underlying surface, it pivots bymeans of the first return device to the neutral position. This movementcan be detected via the sensing device and the missing supporting forcecan be inferred.

The supporting force is preferably measured indirectly by means of thesensing device. It can be provided that the fork is mounted so that itcan move relative to the bearing element, but is forced into apredetermined position by means of a second return device. If the forkthen moves relative to the bearing element, this movement takes placeagainst the force built up by the second return device. Determiningrelative movement between the fork and the bearing element can then beinferred from the force acting on the support roller. In particular, thesecond return device causes the fork to be forced against the bearingelement when the support roller is not in contact with the underlyingsurface and when the fork is moved relative to the bearing elementagainst the force built up by the second return device.

However, the mechanism described above is not limited to a movement ofthe fork relative to the bearing element, but essentially any relativemovement between individual components of the support roller can be usedto determine the supporting force. In addition to or as an alternativeto the mechanism described above, a supporting force can also beindirectly determined by determining the orientation of the fork aboutthe pivot axis using a position recognition device. If this alignmentchanges continuously, it can be assumed that there is an increasedsupporting force and that the support roller is in contact with theunderlying surface. This applies in particular if the fork is forcedinto a predetermined position by the first return device. If the supportroller is deflected from the predetermined position, there is contactwith the underlying surface and a correspondingly predominant supportingforce can be inferred. A hydraulic cylinder can be provided as a shockabsorbing device, which at the same time acts as a control element. Thishydraulic cylinder is preferably connected to the coupling rocker, inparticular the rocker, by means of a lever and is also supported by thesupporting structure. If there is a movement of the coupling rocker orrocker around the rotary axis, this movement is cushioned by means ofthe hydraulic cylinder. The shock absorbing device itself may constitutea third return device by means of which the coupling rocker is forcedinto a third position, but it may also be provided that a separate thirdreturn device, in particular a torsion spring, is provided in order toachieve this function. The use of a hydraulic cylinder offers theadvantage that the control element itself can also be formed by thisdevice. In such a hydraulic cylinder, cushioning is usually achieved bypassing a fluid from one-cylinder chamber to another cylinder chambervia a throttle during a movement of the piston inside the cylinder. Thethrottle can now be formed as a controllable valve, so that a flow ofthe fluid from one-cylinder chamber to the other is prevented, thuscompletely blocking the hydraulic cylinders from the movement of thecoupling rocker around the rotary axis. This locking prevents furtherrotation of the coupling rocker, which could allow the support roller,which is in ground contact, to plunge deeper and cause the vehicle totip over. Other parameters in addition to the supporting force can alsobe included in the control of the control member.

Additional parameters, such as the position of the fork of theindustrial truck, the speed and/or the steering angle, can also beincluded in the calculation of whether the movement of the couplingrocker around the rotary axis should be blocked, in order to achieve thehighest possible level of safety with good driving characteristics atthe same time

In one embodiment, the use of a throttle element and/or pumping mediumto increase the fluid pressure can also be advantageously used tocounteract a tipping over of the vehicle. By increasing the pressurewithin the cylinder chambers, a movement of the coupling rocker iscounteracted by a higher counterforce.

Further features and advantages of the invention result from thefollowing description, in which preferred embodiments of the inventionare explained by means of schematic drawings.

The following applies:

FIG. 1a, 1b are schematic front views of a prior art industrial truck ina neutral and inclined vehicle position;

FIG. 2 is a schematic cross-sectional view of a support roller knownfrom prior art;

FIG. 3a, 3b are schematic cross-sectional views of a support rolleraccording to an embodiment of the invention in an unloaded and a loadedstate;

FIG. 4 is a schematic view of a coupling rocker with a first and asecond support roller and a hydraulic cylinder according to anembodiment of the invention;

FIG. 5a, 5b are hydraulic circuit diagrams for controlling the hydrauliccylinder according to embodiments of the invention;

FIG. 6 is a schematic view of a coupling rocker with a first and asecond support roller and a braking means according to an embodiment ofthe invention;

FIG. 7 is a circuit diagram for the electrical control of the hydraulicvalve according to embodiments the invention; and

FIG. 8 is a flowchart visualizing the execution of a method forstabilizing an industrial truck according to an embodiment of theinvention.

FIG. 1a shows a schematic front view of a vehicle in the form of anindustrial truck 1 known from prior art. The industrial truck 1 shown asan example is a pallet truck with a five-wheel chassis, wherein in FIG.1a only the first and second support rollers 3, 3′ and the drive wheel5, each connected to a supporting structure 4 of the industrial truck 1,are shown. On the industrial truck 1 shown in FIG. 1a , the drive wheel5 is essentially centered between the first and second support rollers3, 3′. The first and second support rollers 3, 3′ are attached to acoupling rocker (not shown) and are connected to each other by thiscoupling rocker. In the prior art the coupling rocker is usuallyattached to the support structure of the industrial truck 1 with springbearings and has the object of distributing the supporting force evenlybetween the first and second support rollers 3, 3′ according to thedriving situation.

FIG. 1b shows a schematic view of the industrial truck 1 shown in FIG.1a in an inclined position. Industrial truck 1 can, for example, inclineaccordingly when cornering tightly with loads held in a high position.If the industrial truck 1 tilts to the side, the coupling rocker isrotated about a rotary axis and the entire spring force of the couplingrocker acts on the first support roller 3 in the example shown. Thesecond support roller 3′ is relieved accordingly and loses contact withan underlying surface 6 on which the industrial truck 1 is moved (shownin FIG. 1b with a dashed border). If the industrial truck 1 tiltsfurther at this point, and if in particular the support roller 3′ movesfurther in the normal direction N of the underlying surface 6, there isa risk of tipping over. In this situation shown in FIG. 1b , thesupporting force with which the support roller 3′ is supported on theunderlying surface 6 is below a first threshold value, since the supportroller 3′ does not touch the underlying surface 6, i.e. the supportroller 3′ is free in the air.

On the other hand, the supporting force of the support roller 3 is abovea threshold value because the support roller 3 is in contact with theunderlying surface 6.

FIG. 2 shows a schematic cross-sectional view of a support roller 3known from prior art. The support roller 3 comprises a fork which isintended to house a wheel 9. Wheel 9 is held in the fork so that it canrotate about a rolling axis R. By means of a bearing formed as a rotarybearing 11 the fork formed as a steering fork 7 can be held with a wheelon the supporting structure of the industrial truck (not shown) by meansof the coupling rocker (not shown) so that it can rotate about a pivotaxis S around its own axis. In the support roller 3 shown, two ballbearings 13 a, 13 b are arranged around the pin 14 of the fork 7 forthis purpose. Wheel 9 is attached to the coupling rocker (not shown) viathe rotary bearing 11, so that wheel 9 can steer too when cornering.

FIG. 3a shows a schematic cross-sectional view of a support rolleraccording to an embodiment of the invention in an unloaded state. Thismeans that the supporting force is below the first threshold value, i.e.the support roller 30 in particular is not in contact with theunderlying surface. As shown in FIG. 3a , many features of the supportroller 30 correspond to the features of the support roller of the priorart shown in FIG. 2. In contrast to the support roller of the prior art,in the embodiment shown the wheel 90 is not only rotatable about thepivot axis S via the steering fork 70 but is also arranged in the rotarybearing 110 along the first direction X, i.e. axially movable to thepivot axis S. In order to achieve improved tracking accuracy, thesteering fork 70 can be pulled into a predetermined position around thepivot axis S by means of an unrepresented first return device. For thispurpose, in the embodiment shown, plain bearings 150 a and 150 b arepressed between the ball bearings 130 a and 130 b and the pin 114 of thesteering fork 70. The plain bearing bushes 150 a, 150 b allow thismovement of the wheel 90 along the direction X. FIG. 3a further showsthat a second return device, which is formed as an elastic means 170 inthe shape of a spring, is arranged at a sliding bush 150 in order tokeep the wheel 90 in an unloaded state vertically pushed out relative tothe rotary bearing 110. The person skilled in the art knows, however,that the displacement can also be effected by means of other returndevices, e.g. a rubber spring.

FIG. 3a shows the first direction X by means of an arrow. In thiscontext, the term “unloaded state” can be used to describe a position inwhich no significant supporting force acts vertically on the wheel 90.For example, this position is assumed when the support roller 30 nolonger makes contact with the underlying surface due to an inclinationof the industrial truck.

FIG. 3a also schematically shows a sensing device 190, which, forexample, can detect the position of the steering fork 70 along the firstdirection X relative to the rotary bearing 110 as a limit switch. Inother embodiments not shown, however, the act of recognizing can becarried out alternatively or in addition to the embodiment showncontactless by means of a Hall sensor and/or a radar sensor.

FIG. 3b shows a schematic cross-sectional view of the support roller 30shown in FIG. 3a in a loaded state. This loaded state can for example beassumed if the support roller 30 has contact with the underlyingsurface. For example, when the weight of the industrial truck (notshown) exerts an axial force on the support roller 30 and the supportroller 30 rests on the underlying surface with a supporting force abovethe second threshold. Between the two positions shown in FIGS. 3a and 3bthere is a distance of approx. 3 mm of the steering fork 70 relative tothe rotary bearing 110. However, the person skilled in the art knowsthat shorter or longer distances can also be covered. The changedposition can then be detected via the sensing device 190. It isimportant to note here that the movement in the X direction takes placeagainst the force generated by the elastic means 170, i.e. the secondreturn device, so that the supporting force acting on the support roller30 can be inferred from the position. When the supporting force isremoved again, the support roller 30 can return to the unloaded stateshown in FIG. 1.

FIG. 4 shows a schematic view of a coupling rocker 210 with a first andsecond support roller 30, 30′. The coupling rocker 210 is mechanicallyarranged between the support rollers 30, 30′ and a bearing 212 of thevehicle's supporting structure. The coupling rocker 210 comprises a 214rocker on which levers 216, 216′ are mounted. Bearings 212 are supportedby levers 216, 216′. The rocker 214 is mounted in bearing 212 so that itcan rotate together with the levers 216, 216′ around a rotary axis D.This rotation is carried out against the force of a third return device218 in the form of a rubber-elastic compression spring.

The coupling rocker 210 further comprises a shock absorbing device inthe form of a 250 hydraulic cylinder. A piston 252 of the hydrauliccylinder 250 is supported by means of a connecting element 230 on therocker 214. The housing of the hydraulic cylinder 250 is supported bythe supporting structure of the vehicle.

In accordance with the invention, i.e. by means of the third returndevice, the coupling rocker 210 is arranged in a spring-loaded way onthe supporting structure of the vehicle. In the embodiment shown, afirst and a second support roller 30, 30′ are arranged at opposite endareas of the coupling rocker 210. In the embodiment shown, the supportrollers with sensing device shown in FIGS. 3a and 3b can be used.However, the person skilled in the art knows that other embodiments mayalso be used, such as support rollers with pressure sensors in thewheels, and/or support rollers comprising Hall sensors, and/or radarsensors for sensing the supporting force, at least indirectly bymeasuring a movement along the first direction.

The hydraulic cylinder 250 fulfils both the function of the shockabsorbing device and the function of the control member. For thispurpose, a throttle in the form of a control-less hydraulic valve isarranged in the hydraulic cylinder. The movement of the fluid within thehydraulic cylinder 250 from a cylinder chamber above the piston to thecylinder chamber below the piston can be controlled via the hydraulicvalve so that in a closed state of the hydraulic valve the movement ofthe hydraulic cylinder 250 is blocked in order to block a verticalmovement, in particular a suspension, of the coupling rocker 210 and thefirst and second support rollers 30, 30′ arranged thereon, and in anopen position to release the movement of the hydraulic cylinder 250 inorder to enable the vertical movement, in particular suspension, of thecoupling rocker 210 and the first and second support rollers 30, 30′arranged thereon. The opening of the valve remains so that thethrottling function is maintained, and cushioning is thus ensured.

FIGS. 5a, 5b show hydraulic circuit diagrams for controlling thehydraulic cylinders 250, 250′ according to the embodiments of theinvention.

In the hydraulic circuit diagram shown in FIG. 5a , the hydrauliccylinder 250, shown as a single-acting hydraulic cylinder, is controlledby means of the hydraulic valve Y1. In the embodiment shown there is noconnection between the cylinder chambers 254 and 256. In the closedposition the hydraulic valve Y1 blocks the movement of the piston 250.However, if hydraulic valve Y1 is in an open position, the movement ofpiston 252 is released. As shown in FIG. 7, hydraulic valve Y1 can beelectrically operated, i.e. electrically closed or opened, by means of acontrol device 260.

In an embodiment not shown, there may be a connection between thecylinder chambers so that the movement or resilience of the couplingrocker in the open position can be enabled so that the hydrauliccylinder can perform the functions of the control member. By installinga throttle in the connection between the cylinder chambers, the functionof the shock absorbing device can also be realized.

The embodiment shown in FIG. 5b can essentially have the structure ofthe embodiment shown in FIG. 5a . In the embodiment shown, the hydrauliccylinder 250′, which is shown as a single-acting hydraulic cylinder, iscontrolled via a throttle element 258 by means of the hydraulic valveY1. The throttle element 258 enables the flow rate of the fluid to becontrolled, thus enabling a particularly cushioned movement when thehydraulic valve Y1 is open. In the embodiment shown in FIG. 5b , aninclination can be actively counteracted by increasing or decreasing thefluid pressure in the hydraulic cylinder 250′. This can be supported bya pump medium. FIG. 5b also shows a non-return valve 259 parallel to thethrottle element 258. This non-return valve 259 can be used to cushion aretracting movement of the cylinder without cushioning an extensionmovement in the opposite direction. This allows the extension movementto take place more quickly.

In the embodiment shown, the cylinders can be extended by increasing thefluid pressure and retracted when the pressure is reduced, in order toadditionally counteract a tipping over. By increasing the pressure, itis possible to counteract a movement ofthe coupling rocker with a highercounterforce.

FIG. 6 is a schematic view of a coupling rocker 210 with a first and asecond support roller 30, 30′ and a braking means 262 according to anembodiment of the invention.

The support rollers 30, 30′ and the fastening of the support rollers 30,30′ of the embodiment of the coupling rocker 210′ shown in FIG. 6 canessentially correspond to the embodiment shown in FIG. 4. However, the210′ coupling rocker shown in FIG. 6 comprises a braking means 262realized as an electromagnetic brake acting as a control member and/orshock absorbing device. In the embodiment shown, the braking means 262can be arranged around the rotary axis D and can also be fixed to thesupporting structure of the vehicle by means of a holding device (notshown).

In particular, in addition to the function of the shock absorbingdevice, the braking means 262 also fulfils the function of the controlmember. In the realization shown as an electromagnetic brake, the brakeblocks a vertical movement, in particular a suspension, of the couplingrocker 210 and of the first and second support rollers 30, 30′ arrangedthereon, when the electromagnetic brake is switched on and/or a currentflows through the coil of the brake. If no current flows through thecoil, the vertical movement, in particular the suspension, of thecoupling rocker 210 and the first and second support rollers 30, 30′arranged on it is released. In the embodiment shown, two brake means262, 262′ are arranged on the rotary axis D of the coupling rocker 210′at opposite ends. Both braking means 262, 262′ can be connected in thesame way in order to enable and inhibit the movement of the couplingrocker 210 at the same time. The person skilled in the art knows,however, that even a single 262 brake is sufficient to lock the 210′coupling rocker.

FIG. 7 shows that the switching contacts S1, S2 are connected in serieswith the sensing devices of the support rollers and connect the coil ofthe hydraulic valve Y1 to a voltage source 270. Thus, when bothswitching contacts S1, S2 are closed, i.e. the two support rollers arein a first position where they are in contact with the underlyingsurface, the hydraulic valve Y1 is controlled so that it is opened in afirst mode and remains open to allow and cushion a movement or springsof the coupling rocker. For example, the inventive control device couldbe structured in this way. The person skilled in the art knows, however,that a programmable logic controller could also be used as a controldevice.

If the industrial truck is tilted and one of the two support rollers onthe coupling rocker is relieved, the signal is interrupted, and thehydraulic cylinder blocks the coupling rocker. Thus, the furtherdeflection of the loaded support roller can be prevented. If bothsupport rollers come into contact with the underlying surface again, thehydraulic valve Y1 is opened again due to the detected increasedsupporting force, so that the drive wheel has sufficient load again,which is required to ensure sufficient traction during starting,steering and braking.

In embodiments not shown, a fluid pressure within the hydraulic cylindercan also be changed by means of the control device or other controlmeans can be used, such as an alignment of a support roller around thepivot axis detected by a positioning means.

The circuit shown in FIG. 7 can for example be used to control thehydraulic cylinders shown in FIGS. 5a and 5b . However, the brake fluidshown in FIG. 6 and described above can also be controlled by means ofsuch a circuit if instead of the hydraulic valve coil, the brake fluidcoil is connected in the circuit.

FIG. 8 shows a method 1000 for stabilizing an industrial truck accordingto an embodiment of the invention. The method comprises the followingsteps:

detecting 1010 a supporting force with which the support roller issupported on an underlying surface, wherein in the case of at least onefirst supporting force the support roller is in contact with theunderlying surface, and in the case of at least one second supportingforce the support roller is not in contact with the underlying surface;andcontrolling 1020 of a control member as a function of the detectedsupporting force, wherein a rotation of the coupling rocker 210 and/orthe support roller about a rotary axis is at least partially preventedby means of the control member upon detecting the second supportingforce.

The features depicted in the above description, claims and figures maybe essential to the invention in its various embodiments, eitherindividually or in any combination.

LIST OF REFERENCE NUMERALS

-   1 industrial truck-   3, 3′, 30, 30′ support roller-   4 supporting structure-   5 drive wheel-   6 underlying surface-   7, 70, 70′ steering fork-   9, 90, 90′ wheel-   11, 110, 110′ rotary bearing-   13 a, 13 b, 130 a, 130 b ball bearing-   14, 114 pin-   150 a, 150 b plain bearing-   170 elastic means-   190 sensing device-   210 coupling rocker-   212 bearing-   214 rocker-   216, 216′ lever-   218 return device-   230 connecting means-   250, 250′ hydraulic cylinder-   252, 252′ piston-   254, 256, 254′, 256′ cylinder chamber-   258 throttle element-   259 non-return valve-   260 control device-   262 braking means-   270 voltage source-   1000 method for stabilizing an industrial truck-   1010 detecting a position-   1020 controlling a positioning cylinder-   S1, S2 switching contact-   Y1 hydraulic valve-   S pivot axis-   R rolling axis-   X direction-   N normal direction-   D rotary axis

1. A support roller (30, 30′) for supporting a vehicle on an underlyingsurface, comprising at least one bearing element which is at leastindirectly connectable to at least one supporting structure of thevehicle, at least one fork connected to the bearing element, and atleast one wheel (90, 90′) which is mounted in the fork so as to berotatable about a first rolling axis (R) and can be brought into contactwith the underlying surface, wherein the support roller furthercomprises at least one sensing device (190) for sensing at least onesupporting force with which the wheel (90, 90′) is supported on theunderlying surface, and wherein a force acting between at least a firstelement and at least a second element is detectable by means of thesensing means.
 2. The support roller (30, 30′) according to claim 1,characterized in that (i) the rolling axis (R) is perpendicular to anormal direction (N) of the underlying surface and/or that thesupporting structure is formed at least in certain areas by a part ofthe vehicle body; (ii) the bearing element is formed in the form of atleast one rotary bearing (110, 110′) and that a rotation of the forkabout a pivot axis (S) running substantially perpendicularly to therolling axis (R) is possible by means of the rotary bearing (110, 110′),wherein in particular the rolling axis (R) and the pivot axis (S)intersect or run obliquely relative to one another and/or the forkand/or the rolling axis (R) can be forced by means of at least one firstreturn device into at least one predetermined position relative to thebearing element and/or the supporting structure, preferably with regardto the pivot axis (S), and/or, (iii) that a movement of at least onefirst element relative to at least one second element is detectable bymeans of the sensing device (190), preferably that a, in particularlinear, movement in a first direction running perpendicularly to therolling axis (R) and/or parallel to the pivot axis (S), and/or a forceacting by means of the sensing device (190) a tensile force, acompressive force and/or shear force is detectable.
 3. (canceled) 4.(canceled)
 5. The support roller (30, 30′) according to claim 1,characterized in that (a) that the first element is selected from thegroup comprising the roller, a bearing axle of the roller mounted in thefork, the fork, at least one connecting means of the fork to the bearingelement, such as a pin (114), and the bearing element, and/or the secondelement is selected from the group comprising the bearing axle, thefork, the connecting means, the bearing element and the supportingstructure, (b) the second element, in particular the bearing element, isadapted to keep the first element, in particular the fork, movable alongthe first direction (X), preferably the second element (110, 110′) isadapted to allow a movement of the first element of up to 5 mm, inparticular of 3 mm, preferably relative to the second element, and/or(c) the first element, in particular the fork and/or the connectingmeans, is forcible into a first position, in particular in a direction(X) towards the second element, by means of at least one second returndevice.
 6. (canceled)
 7. (canceled)
 8. The support roller (30, 30′)according to claim 2, characterized in that the first return deviceand/or the second return device comprises at least one elastic means(170), at least one compression spring, at least one helical spring, atleast one pneumatic spring, at least one hydraulic spring and/or atleast one gas pressure spring, and/or the sensing device (190) isarranged at least in certain areas in the bearing element and/or on theside of the bearing element, preferably the pivot bearing (110, 110′),facing away from the fork and/or the wheel (90, 90′).
 9. (canceled) 10.The support roller (30, 30′) according to claim 1, characterized by atleast one position recognition device by means of which an alignment ofthe fork, the bearing axis and/or the wheel (90, 90′) about the pivotaxis (S) and/or relative to the underlying surface is determinable. 11.The support roller (30, 30′) according to claim 1, characterized in thatthe sensing device (190) and/or the position recognition devicecomprises and/or comprise at least one sensor means, in particularcomprising at least one limit switch, at least one strain gauge sensor,at least one pressure sensor, at least one Hall sensor, at least oneradar sensor, at least one ultrasonic sensor, at least one distancesensor, at least one echo sounder sensor, at least one acoustic sensor,at least one optical sensor, at least one electromagnetic sensor, and/orat least one magnetic sensor, or and/or the first position and/or atleast a second position of the first element relative to the secondelement is detectable by means of the sensing device (190).
 12. Avehicle, in particular an industrial truck, comprising at least onesupport roller (30, 30′) according to claim
 1. 13. The vehicle accordingto claim 12, characterized in that the vehicle further comprises atleast one coupling rocker (210), wherein the coupling rocker (210) isarranged mechanically between the supporting structure and the supportroller (30, 30′) and the coupling rocker (210) has at least one rocker(214) mounted rotatably about at least one rotary axis (D) and a lever(216, 216′) which is operatively connected to the rocker (214), whereinthe support roller (30, 30′), in particular the bearing element, issupported at the end of the lever (216, 216′) away from the pivot axis(S) and/or the rocker (214), wherein furthermore the lever (216, 216′)is preferably surrounded by the rocker (214) and/or is formed integrallywith the rocker (214) at least in certain areas, wherein the couplingrocker (210) comprises at least one third return device by means ofwhich the rocker (214) and/or the lever (216, 216′) is/are forcible intoat least one third position, wherein the third return device preferablycomprises at least one torsion spring, at least one helical spring, atleast one tension spring, at least one thrust spring, at least one shearspring, at least one rubber-elastic element, at least one spiral springand/or at least one gas pressure spring.
 14. (canceled)
 15. The vehicleaccording to claim 13, characterized in that (i) the coupling rocker(210) comprises at least one shock absorbing device, wherein a movement,in particular of the lever (216, 2161 the support roller (30, 30′)and/or the rocker (214) about the rotary axis (D) can be cushioned bymeans of the shock absorbing device, and/or (ii) the vehicle ischaracterized by at least one control member, which is in particular inoperative connection with the shock absorbing device, wherein amovement, in particular of the lever (216, 2161 the support roller (30,30′) and/or the rocker (214), about the rotary axis (D) by means of thecontrol member is reducible, preferably suppressible, wherein thecontrol member is preferably at least in certain areas enclosed by theshock absorbing device.
 16. (canceled)
 17. The vehicle according toclaim 15 or 16, characterized in that the shock absorbing device and/orthe control member comprises at least one cylinder, in particular ahydraulic cylinder (250), with at least one piston (252) movable withinthe cylinder, the cylinder being operatively connected to the lever(216, 216′), the support roller (30, 30′), in particular the bearingelement, and/or the rocker (214), preferably via a connecting element(230) extending at least in a radial direction with respect to therotary axis (D), and the piston (252) being operatively connected to thesupporting structure or the piston (252) being operatively connected tothe lever (216, 216′), the rocker (214), the support roller (30, 30′),the bearing element and/or the connecting element (230) and the cylinderbeing operatively connected to the supporting structure.
 18. The vehicleaccording to claim 17, characterized in that the control membercomprises at least one control element, the control element preferablycomprises at least one control valve and/or, by means of closing thecontrol element, a movement of the shock absorbing device and/or of thecontrol member and/or a movement, in particular of the rocker (214), ofthe lever (216), 216′) and/or the support roller (30, 30′), about therotary axis is prevented and, when the control element is opened, amovement of the shock absorbing device and/or of the control memberand/or a movement, in particular of the rocker (214), of the lever (216,216′) and/or of the support roller (30, 30′), about the rotary axis (D)is released.
 19. The vehicle according to claim 18, characterized inthat (i) the cylinder preferably comprises a single-acting cylinder andthe control element comprises a throttle element (258) adapted tocontrol the flow rate of at least one fluid, preferably a hydraulicfluid, a gas and/or air into the cylinder, preferably to allow shockabsorbing, preferably the control element being adapted to control thethrottle element (258) as a function of the supporting force detected bythe sensing device in order to increase the fluid pressure in order toavoid a reduction of the supporting force below a predetermined value,or (ii) the cylinder, in particular the hydraulic cylinder (250),comprises at least two-cylinder chambers (254, 256) connectable to eachother via at least one throttle, the fluid being movable in particularbetween the cylinder chambers (254, 256), in particular by movement ofthe piston (252).
 20. (canceled)
 21. The vehicle according to claim 15,characterized in that the control member comprises at least one brakingmeans (262), in particular an electromagnetic brake, a mechanical brake,an adhesive and/or positive brake, the braking means being operativelyconnected, preferably on the one hand, to the rocker (214) and/or to thesupport roller (30, 30′) and/or, on the other hand, to the supportingstructure, wherein (a) the braking means (262) is arranged at least incertain areas, preferably circularly revolving about the rotary axis (D)of the coupling rocker (210), and/or (b) the vehicle is characterized byat least one control device operatively connected to the control memberand/or the shock absorbing device, the control device comprising atleast one power supply, in particular an electrical voltage supplyand/or a device for storing and/or emitting mechanical energy, of thebraking means (262), and wherein when energy is emitted from the controldevice to the control member a movement of the shock absorbing deviceand/or of the control member and/or a movement, in particular of therocker (214) and/or of the support roller (30, 30′), about the rotaryaxis (D) is prevented, and when the emission of energy is interrupted amovement of the shock absorbing device and/or of the control memberand/or a movement, in particular of the rocker (214) and/or of thesupport roller (30, 301 about the rotary axis (D) is enabled. 22.(canceled)
 23. (canceled)
 24. The vehicle according to claim 12,characterized by at least one control device operatively connected tothe sensing device (190), the position recognition device, the controldevice and/or the control member, preferably the control element,wherein the control member can preferably be influenced by means of thecontrol device in such a way that the movement about the rotary axis (D)is reduced, is preferably prevented when, by means of the sensing device(190), a supporting force is sensed which corresponds to a missingcontact between the support roller (30, 30′) and the underlying surfaceand/or the movement about the rotary axis (D) is at least partiallyreleased when, by means of the sensing device (190), a supporting forceis sensed which corresponds to an existing contact between the supportroller (30, 30′) and the underlying surface, wherein the control deviceinfluences the control member as a function of a position of at leastone lifting fork of the vehicle, in particular relative to theunderlying surface, a speed of the vehicle and/or a steering angle ofthe vehicle.
 25. (canceled)
 26. The vehicle according to claim 12,characterized in that (i) the control member comprises at least one pumpmeans for increasing a fluid pressure in the cylinder, in particular thecylinder chambers (254, 256), preferably the control device beingadapted to control the pump means as a function of the supporting forcedetected by the sensing device (190) in order to increase the fluidpressure in order to avoid a reduction of the supporting force below apredetermined value, (ii) the vehicle is characterized by a plurality ofsupport rollers (30, 30′) according to any of claims 1 to 11, whereinthe coupling rocker (210) preferably comprises a plurality of levers(216, 216′), preferably arranged on the rocker (214), surrounded by therocker (214) and/or at least in certain areas integrally formed with therocker (214), and/or (iii) the vehicle is formed as an industrial truckand/or as a pallet truck with at least one drive wheel, in particular apallet truck with five-wheel chassis.
 27. (canceled)
 28. (canceled) 29.A method (1000) for stabilizing a vehicle according to claim 12, havinga coupling rocker (210) and at least one support roller (30, 30′)according to claim 1, having the following steps: detecting 1010 asupporting force with which the support roller (30, 30′) is supported onan underlying surface, wherein in the case of at least one firstsupporting force the support roller (30, 30′) is in contact with theunderlying surface, and in the case of at least one second supportingforce the support roller (30, 30′) is not in contact with the underlyingsurface; and controlling (1020) of a control member (250) as a functionof the detected supporting force, wherein a rotation of the couplingrocker (210) and/or the support roller (30, 30′) about a rotary axis (D)is at least partially prevented by means of the control member upondetecting the second supporting force.
 30. The method (1000) accordingto claim 29, characterized in that, (a) when the first supporting forceis recognized, a movement about the rotary axis (D) is cushioned bymeans of at least one shock absorbing device, (b) the cushioning andsuppression of the movement about the rotary axis (D) is carried out bymeans of a device which at least in part comprises the control memberand the shock absorbing device, in particular the shock absorbing deviceand the control member are at least in part formed integrally, and/or(c) the suppression of the movement about the rotary axis (D) isachieved by suppressing a movement of the shock absorbing device and/orat least a third return device.
 31. (canceled)
 32. (canceled)